EP0165095A1 - Hydraulic antivibration mounting - Google Patents

Hydraulic antivibration mounting Download PDF

Info

Publication number
EP0165095A1
EP0165095A1 EP85400815A EP85400815A EP0165095A1 EP 0165095 A1 EP0165095 A1 EP 0165095A1 EP 85400815 A EP85400815 A EP 85400815A EP 85400815 A EP85400815 A EP 85400815A EP 0165095 A1 EP0165095 A1 EP 0165095A1
Authority
EP
European Patent Office
Prior art keywords
rigid
ring
foot
elastic wall
sole
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP85400815A
Other languages
German (de)
French (fr)
Other versions
EP0165095B1 (en
Inventor
Francois Bodin
Pierre Jouade
Daniel Le Guillant
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hutchinson SA
Original Assignee
Hutchinson SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=9303712&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0165095(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hutchinson SA filed Critical Hutchinson SA
Priority to AT85400815T priority Critical patent/ATE31353T1/en
Publication of EP0165095A1 publication Critical patent/EP0165095A1/en
Application granted granted Critical
Publication of EP0165095B1 publication Critical patent/EP0165095B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like

Definitions

  • the invention relates to anti-vibration devices intended to be interposed for the purposes of support and damping between two rigid elements, the damping involving the delivery of a liquid through a throttled passage, and the relative displacements to dampen two rigid elements comprising on the one hand relatively large amplitude oscillations (that is to say greater than 1 mm) at relatively low frequency (that is to say less than 20 Hz) and on the other hand vibrations of relatively small amplitude (that is to say less than 0.5 mm) at relatively high frequency (that is to say greater than 20 Hz).
  • such supports can be mounted between a vehicle chassis and the engine of this vehicle, the relatively large oscillations to be absorbed being those created by the irregularities and variations in gradient of the ground during the movement of the vehicle on this ground and the vibrations to be damped being those due to the operation of the engine.
  • the invention relates more particularly, among the supports of the kind in question, those which consist of a sealed housing interposed between the two rigid elements, housing comprising two rigid parts which can be joined respectively to the two rigid elements, a first elastic wall connecting in a manner waterproof one of the two rigid parts to a rigid annular reinforcement forming part of the second part, this first wall deli mitting with the first part one of the two axial ends of the shoemaker and ensuring the role of support between the two parts, for which it has good resistance to axial compression, a second elastic wall carried in a sealed manner by the frame annular and delimiting the second axial end of the case, a deformable partition also carried in a sealed manner by the annular reinforcement, between the two elastic walls, and dividing the interior of the case into two chambers, namely a working chamber between the partition and the first elastic wall and a compensation chamber between the partition and the second elastic wall, these two chambers communicating with each other by the throttled passage above, means for limiting to a small amplitude, that is to say less than 1
  • a vibration of high frequency and of small amplitude exerted between the two rigid elements generates corresponding relative displacements of the two rigid parts, which are transmitted to the deformable partition by the liquid contained in the working chamber and result in a rapid succession of alternative deformations of this partition perpendicular to itself, of amplitude less than the maximum possible value: the dimensions of the partition are chosen to be sufficient so that it can thus absorb the movements indicated without the liquid being discharged through the passage throttled in opposite directions in synchronism with the vibration.
  • the supported mass (motor or other) is connected to the bearing structure (vehicle chassis) only by the first elastic walls of these supports.
  • the object of the invention is, above all, to remedy this drawback by limiting by abutment the deformations in question. ''
  • the invention includes, apart from these main provisions, certain other provisions which are preferably used at the same time and which will be more explicitly discussed below.
  • Figure 1 of this drawing shows in axial section an anti-vibration support established in accordance with the invention.
  • Figure 2 similarly shows a variant of a portion of this support also according to the invention.
  • Said support is designed to be interposed ver- tically between a rigid carrier member consisting of a vehicle chassis and a rigid supported member consisting of an internal combustion engine.
  • top, bottom, top and bottom used in the description which follows are by way of nonlimiting example because the support described can perfectly be used in reverse of the direction adopted for this description.
  • a deformable partition 9 divides the interior of the housing into two chambers, namely an upper "working” chamber A, on the side of the wall 6, and a lower "compensating" chamber B on the side of the wall 8.
  • the wall 9 is constituted by a flexible membrane whose edge is fixed to a rigid annular seat 11 itself extended externally by an annular flange 11 1 .
  • the passage 1.0 is here constituted by a curvilinear channel hollowed out in the flange 11 1 , channel extending in an arc of circle between 180 and 300 ° and connected at its two ends with respectively the two chambers A and B.
  • Means known per se are also provided for limiting the deformations of the membrane 9 to a small amplitude, namely less than 1 mm.
  • stop means are provided for limiting the deformations of the frusto-conical wall 6 in any direction and thus prohibit, on the one hand, deterioration or even ruptures, of this wall 6, and on the other hand unfortunate impacts between the supported engine and the walls of the passenger compartment of this engine.
  • the foot 13 is advantageously constituted by a cylindrical pin housed in a complementary recess of the body 3 and forming a single piece with the stud 5, which extends this pin upwards.
  • the protruding sole 14 is advantageously in the form of a plate which can be integral with the pin 13 or be attached axially against the end of this pin.
  • the cross section of the sole 14 is clearly greater than that of the free passage hollowed out in the ring 12.
  • the upper face of the protruding margin of the sole 14, that is to say its face facing the ring 12, is coated with an annular cushion 15 of rubber or similar elastic material.
  • a sleeve 16 also made of rubber or the like, is provided on the peripheral face of the foot 13 or of the sole 14, capable of abutting radially against a facing bearing: this is the case of the sole 14 in the figure 1 and of the base of the foot 13 connected to the sole in FIG. 2.
  • the radial clearance j between the foot 13 and the ring 12 must be sufficient so that the passage of the damping liquid at this level is not throttled to the point of adjusting the operation of the shock absorber.
  • This game must on the other hand be small enough so that the ring 12 can effectively play its role of abutment, specified below, in all directions.
  • the ring 12 is formed, not by a simple flat washer, but by an inner flat washer 12 1 connected to an outer flat washer 12 2 axially offset with respect to the inner washer, by l 'through an annular connection portion 12 3 having an S profile.
  • This stop is first established gradually through the interposition of the cushion 15, then it completely interrupts the tensile deformation of the wall 6 when said cushion 15 is completely crushed.
  • This support has over those previously known the important advantage of ensuring a very solid anchoring of the first rigid part on the second, that is to say, in the application cited by way of example, of the motor on the chassis of the vehicle, in view of the limitation by elastic stop which is imposed, in such a support, on the deformations of the wall 6 during the exercise of abnormally high stresses on the supported mass.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Lubricants (AREA)
  • Springs (AREA)
  • External Artificial Organs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Absorbent Articles And Supports Therefor (AREA)
  • Vibration Prevention Devices (AREA)
  • Supports For Pipes And Cables (AREA)
  • Body Structure For Vehicles (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention relates to an antivibration support to be inserted between the frame and the engine of a vehicle. The support comprises two deformable chambers filled with liquid, separated by a deformable partition, and communicating with one another through a restricted passage, namely an operating chamber whose lateral wall forms a support and joins two rigid parts fixed respectively to the frame and to the engine, and a compensating chamber. When abnormally high thrusts are applied to the engine, the deformations of the wall are limited by abutment, against a ring immersed in the operating chamber and borne by the first rigid part, of a central foot fast to the second rigid part, and passing with clearance through the ring and/or of an overlapping sole terminating this foot.

Description

L'invention concerne les dispositifs antivibra- toires destinés à être interposés aux fins de support et d'amortissement entre deux éléments rigides, l'amortissement faisant intervenir le refoulement d'un liquide à travers un passage étranglé, et les déplacements relatifs à amortir des deux éléments rigides comprenant d'une part des oscillations de relativement grande amplitude (c'est-à-dire supérieure au mm) à fréquence relativement basse (c'est-à-dire inférieure à 20 Hz) et d'autre part des vibrations de relativement faible amplitude (c'est-à-dire inférieure à 0,5 mm) à fréquence relativement élevée (c'est-à-dire supérieure à 20 Hz).The invention relates to anti-vibration devices intended to be interposed for the purposes of support and damping between two rigid elements, the damping involving the delivery of a liquid through a throttled passage, and the relative displacements to dampen two rigid elements comprising on the one hand relatively large amplitude oscillations (that is to say greater than 1 mm) at relatively low frequency (that is to say less than 20 Hz) and on the other hand vibrations of relatively small amplitude (that is to say less than 0.5 mm) at relatively high frequency (that is to say greater than 20 Hz).

A titre d'exemple non limitatif, on indique que de tels supports peuvent être montés entre un châssis de véhicule et le moteur de ce véhicule, les oscillations relativement amples à amortir étant celles créées par les irrégularités et variations de déclivité du sol lors de la circulation du véhicule sur ce sol et les vibrations à amortir étant celles dues au fonctionnement du moteur.By way of nonlimiting example, it is indicated that such supports can be mounted between a vehicle chassis and the engine of this vehicle, the relatively large oscillations to be absorbed being those created by the irregularities and variations in gradient of the ground during the movement of the vehicle on this ground and the vibrations to be damped being those due to the operation of the engine.

L'invention concerne plus particulièrement, parmi les supports du genre en question, ceux qui sont constitués par un boîtier étanche interposé entre les deux éléments rigides, boîtier comportant deux pièces rigides solidarisables respectivement avec les deux éléments rigides, une première paroi élastique reliant de façon étanche l'une des deux pièces rigides à une armature annulaire rigide faisant partie de la seconde piêce, cette première paroi délimitant avec la première pièce l'une des deux extrémités axiales du bottier et assurant le rôle de support entre les deux pièces, ce pour quoi elle présente une bonne résistance à la compression axiale, une seconde paroi élastique portée de manière étanche par l'armature annulaire et délimitant la seconde extrémité axiale du bottier, une cloison déformable également portée de manière étanche par l'armature annulaire, entre les deux parois élastiques, et divisant l'intérieur du bottier en deux chambres, savoir une chambre de travail comprise entre la cloison et la première paroi élastique et une chambre de compensation comprise entre la cloison et la seconde paroi élastique, ces deux chambres communiquant entre elles par le passage étranglé ci-dessus, des moyens pour limiter à une amplitude faible, c'est-à-dire inférieure à 1 mm, les déformations de la cloison selon la direction axiale perpendiculaire à son plan moyen, et une masse liquide remplissant les deux chambres ainsi que le passage étranglé.The invention relates more particularly, among the supports of the kind in question, those which consist of a sealed housing interposed between the two rigid elements, housing comprising two rigid parts which can be joined respectively to the two rigid elements, a first elastic wall connecting in a manner waterproof one of the two rigid parts to a rigid annular reinforcement forming part of the second part, this first wall deli mitting with the first part one of the two axial ends of the shoemaker and ensuring the role of support between the two parts, for which it has good resistance to axial compression, a second elastic wall carried in a sealed manner by the frame annular and delimiting the second axial end of the case, a deformable partition also carried in a sealed manner by the annular reinforcement, between the two elastic walls, and dividing the interior of the case into two chambers, namely a working chamber between the partition and the first elastic wall and a compensation chamber between the partition and the second elastic wall, these two chambers communicating with each other by the throttled passage above, means for limiting to a small amplitude, that is to say less than 1 mm, the deformations of the partition in the axial direction perpendicular to its mean plane, and a liquid mass filling the two chambers as well as the passa strangled age.

Avec un tel support, une vibration de fréquence élevée et de faible amplitude exercée entre les deux éléments rigides engendre des déplacements relatifs correspondants des deux pièces rigides, lesquels sont transmis à la cloison déformable par le liquide contenu dans la chambre de travail et se traduisent par une succession rapide de déformations alternatives de cette cloison perpendiculairement à elle-même, d'amplitude inférieure à la valeur maximum possible : les dimensions de la cloison sont choisies suffisantes pour que celle-ci puisse ainsi absorber les déplacements signalés sans que le liquide soit refoulé à travers le passage étranglé selon des sens opposés en synchronisme avec la vibration.With such a support, a vibration of high frequency and of small amplitude exerted between the two rigid elements generates corresponding relative displacements of the two rigid parts, which are transmitted to the deformable partition by the liquid contained in the working chamber and result in a rapid succession of alternative deformations of this partition perpendicular to itself, of amplitude less than the maximum possible value: the dimensions of the partition are chosen to be sufficient so that it can thus absorb the movements indicated without the liquid being discharged through the passage throttled in opposite directions in synchronism with the vibration.

Au contraire, pour les oscillations d'amplitude plus élevée et de fréquence plus basse, l'amplitude des déformations correspondantes de la cloison atteint sa valeur maximum possible et le liquide est alors refoulé à travers le passage étranglé, ce qui assure l'amortissement hydraulique de ce liquide par son étranglement dans ce passageOn the contrary, for oscillations of higher amplitude and lower frequency, the amplitude of the corresponding deformations of the partition reaches its maximum possible value and the liquid is then discharged through the throttled passage, which ensures hydraulic damping of this liquid by its constriction in this passage

Avec les modes de réalisation actuels des supports du genre en question, la masse supportée (moteur ou autre) n'est reliée à la structure portante (châssis du véhicule) que par les premières parois élastiques de ces supports.With the current embodiments of supports of the kind in question, the supported mass (motor or other) is connected to the bearing structure (vehicle chassis) only by the first elastic walls of these supports.

Il peut donc arriver que certaines sollicitations anormalement élevées exercées sur la masse supportée, telles que celles dues à des décélérations ou accélérations brusques, se traduisent par des déformations excessives de ces parois pouvant entraîner leur arrachement ou leur rupture et engendrer des chocs générateurs de dommages entre ladite masse supportée et son environnement immédiat.It can therefore happen that some abnormally high stresses exerted on the supported mass, such as those due to sudden decelerations or accelerations, result in excessive deformations of these walls which can cause their tearing or their rupture and generate shocks generating damage between said supported mass and its immediate environment.

L'invention a pour but, surtout, de remédier à cet inconvénient en limitant par butée les déformations en question. 'The object of the invention is, above all, to remedy this drawback by limiting by abutment the deformations in question. ''

A cet effet les supports du genre en question selon l'invention sont essentiellement caractérisés en ce qu'ils comprennent :

  • - un anneau rigide porté par l'armature annulaire, entre la cloison déformable et la première paroi élastique, anneau dont le bord interne plonge dans la chambre de travail,
  • - et un pied prolongeant la première pièce rigide vers l'intérieur de la chambre de travail, pied traversant avec jeu l'anneau rigide et terminé au-delà de cet anneau par une semelle débordante dont la section droite est supérieure à la section de passage de l'anneau.
To this end, the supports of the genre in question according to the invention are essentially characterized in that they comprise:
  • - a rigid ring carried by the annular reinforcement, between the deformable partition and the first elastic wall, ring whose internal edge plunges into the working chamber,
  • - And a foot extending the first rigid part towards the interior of the working chamber, foot crossing with play the rigid ring and terminated beyond this ring by an overhanging sole whose cross section is greater than the passage section of the ring.

Dans des modes de réalisation préférés, on a recours en outre à l'une et/ou à l'autre des dispositions suivantes :

  • - les faces, du pied et/ou de la semelle, susceptibles de venir en butée contre des portées en regard de l'anneau rigide ou d'autres composants du support, sont revêtues d'un coussin de caoutchouc ou matériau analogue,
  • - le pied est constitué par un-pion cylindrique et la semelle par une plaquette rapportée axialement sur l'extrémité libre de ce pion,
  • - l'anneau rigide comporte une rondelle plate intérieure disposée à l'intérieur de la première paroi élastique et raccordée par une portion annulaire incurvée en S à une rondelle plate extérieure décalée axialement par rapport à la rondelle intérieure et serrée axialement entre la première paroi élastique et la portion périphérique du siège de la cloison déformable.
In preferred embodiments, use is also made of one and / or the other of the following arrangements:
  • the faces of the foot and / or of the sole, which may come into abutment against bearing surfaces facing the rigid ring or other components of the support, are covered with a cushion of rubber or similar material,
  • - the base consists of a cylindrical pin and the sole by a plate axially attached to the free end of this pin,
  • - The rigid ring has an internal flat washer disposed inside the first elastic wall and connected by an annular curved portion in S to an external flat washer axially offset relative to the internal washer and axially clamped between the first elastic wall and the peripheral portion of the seat of the deformable partition.

L'invention comprend, mises à part ces dispositions principales, certaines autres dispositions qui s'utilisent de préférence en même temps et dont il sera plus explicitement question ci-après.The invention includes, apart from these main provisions, certain other provisions which are preferably used at the same time and which will be more explicitly discussed below.

Dans ce qui suit, l'on va décrire des modes de réalisation préférés de l'invention en se référant au dessin ci-annexé d'une manière bien entendu non limitative.In what follows, we will describe preferred embodiments of the invention with reference to the accompanying drawing in a manner of course not limiting.

La figure 1, de ce dessin, montre en coupe axiale un support antivibratoire établi conformément à l'invention.Figure 1 of this drawing shows in axial section an anti-vibration support established in accordance with the invention.

La figure 2 montre semblablement une variante d'une portion de ce support également conforme à l'invention.Figure 2 similarly shows a variant of a portion of this support also according to the invention.

Ledit support est destiné à être interposé ver- ticalement entre un organe porteur rigide constitué par un châssis de véhicule et un organe supporté rigide constitué par un moteur à combustion interne.Said support is designed to be interposed ver- tically between a rigid carrier member consisting of a vehicle chassis and a rigid supported member consisting of an internal combustion engine.

Les termes "haut, bas, supérieur et inférieur" utilisés dans la description qui suit le sont à titre d'exemple non limitatif car le support décrit peut parfaitement être utilisé à l'envers du sens adopté pour cette description.The terms "top, bottom, top and bottom" used in the description which follows are by way of nonlimiting example because the support described can perfectly be used in reverse of the direction adopted for this description.

Le support considéré se présente sous la forme générale d'un boîtier étanche comportant :

  • - une cuvette inférieure rigide 1 dont le bord incurvé Il constitue une virole ou armature annulaire permettant d'assembler l'ensemble par sertissage, comme il sera exposé plus loin, ladite cuvette étant solidarisée, notamment par soudure, avec une patte 2 facile à monter sur le châssis du véhicule,
  • - un chapeau rigide comportant un corps tronconiqus plein 3 évasé vers le haut, lui-même coiffé par un disque 4 et prolongé par un goujon fileté 5 en attente,
  • - une paroi tronconique épaisse et étanche 6 en caoutchouc ou matériau élastique analogue présentant une bonne résistance à la compression axiale et à la flexion transversale et adhérée respectivement sur le corps 3 et sur un renfort annulaire 7 profilé en Z, renfort lui-même lié de façon étanche à la virole 11,
  • - et une paroi élastique étanche 8 dont le pourtour est également lié de façon étanche à la virole 11, paroi constituée de préférence par une membrane flexible mince plissée selon des anneaux concentriques.
The support considered is in the general form of a waterproof case comprising:
  • - a rigid lower shell 1, the curved edge I l is a ferrule or annular armature for assembling the assembly by crimping as will be explained below, said bowl being secured, in particular by welding, with a tab 2 which is easy to mount on the chassis of the vehicle,
  • a rigid cap comprising a full frustoconical body 3 flared upwards, itself capped by a disc 4 and extended by a threaded stud 5 pending,
  • - A thick, sealed frustoconical wall 6 of rubber or similar elastic material having good resistance to axial compression and to transverse bending and adhered respectively to the body 3 and to an annular reinforcement 7 Z-shaped, reinforcement itself linked to sealed to the ferrule 1 1 ,
  • - And a waterproof elastic wall 8 whose periphery is also tightly connected to the ferrule 1 1 , wall preferably constituted by a thin flexible membrane pleated according to concentric rings.

Une cloison déformable 9 divise l'intérieur du boîtier en deux chambres, savoir une chambre supérieure "de travail" A, du côté de la paroi 6, et une chambre inférieure "de compensation" B du côté de la paroi 8.A deformable partition 9 divides the interior of the housing into two chambers, namely an upper "working" chamber A, on the side of the wall 6, and a lower "compensating" chamber B on the side of the wall 8.

Ces deux chambres A et B sont remplies de liquide et la communication entre elles est assurée en permanence à travers un passage étranglé 10.These two chambers A and B are filled with liquid and communication between them is ensured permanently through a constricted passage 10.

Dans le mode de réalisation illustré, la paroi 9 est constituée par une membrane flexible dont le bord est fixé sur un siège annulaire rigide 11 lui-même prolongé extérieurement par un rebord annulaire 111.In the illustrated embodiment, the wall 9 is constituted by a flexible membrane whose edge is fixed to a rigid annular seat 11 itself extended externally by an annular flange 11 1 .

Le passage 1.0 est ici constitué par un canal curviligne évidé dans le rebord 111, canal s'étendant selon un arc de cercle compris entre 180 et 300° et raccordé à ses deux extrémités avec respectivement les deux chambres A et B.The passage 1.0 is here constituted by a curvilinear channel hollowed out in the flange 11 1 , channel extending in an arc of circle between 180 and 300 ° and connected at its two ends with respectively the two chambers A and B.

Des moyens connus en soi sont en outre prévus pour limiter les déformations de la membrane 9 à une amplitude faible, savoir inférieure à 1 mm.Means known per se are also provided for limiting the deformations of the membrane 9 to a small amplitude, namely less than 1 mm.

On prévoit en outre, selon l'invention, des moyens de butée permettant de limiter les déformations de la paroi tronconique 6 dans n'importe quelle direction et d'interdire ainsi d'une part les détériorations, voire les ruptures,de cette paroi 6, et d'autre part les chocs fâcheux entre le moteur supporté et les parois de l'habitacle de ce moteur.In addition, according to the invention, stop means are provided for limiting the deformations of the frusto-conical wall 6 in any direction and thus prohibit, on the one hand, deterioration or even ruptures, of this wall 6, and on the other hand unfortunate impacts between the supported engine and the walls of the passenger compartment of this engine.

Ces moyens de butée comprennent

  • - d'une part, un anneau rigide 12 dont le bord intérieur s'étend dans la chambre de travail A,
  • - et d'autre part, un pied 13 prolongeant axialement vers le bas le corps 3, pied traversant avec un jeu radial j l'anneau 12 et terminé au-delà de cet anneau par une semelle 14 débordante transversalement.
These stop means include
  • on the one hand, a rigid ring 12, the inner edge of which extends into the working chamber A,
  • - And on the other hand, a foot 13 extending the body 3 axially downward, foot crossing with a radial clearance at the ring 12 and terminated beyond this ring by a sole 14 projecting transversely.

Le pied 13 est avantageusement constitué par un pion cylindrique logé dans un évidement complémentaire du corps 3 et formant une_seule pièce avec le goujon 5, qui prolonge ce pion vers le haut.The foot 13 is advantageously constituted by a cylindrical pin housed in a complementary recess of the body 3 and forming a single piece with the stud 5, which extends this pin upwards.

La semelle débordante 14 se présente avantageusement sous la forme d'une plaquette qui peut faire corps avec le pion 13 ou être rapportée axialement contre l'extrémité de ce pion.The protruding sole 14 is advantageously in the form of a plate which can be integral with the pin 13 or be attached axially against the end of this pin.

La section transversale de la semelle 14 est nettement supérieure à celle du passage libre évidé dans l'anneau 12.The cross section of the sole 14 is clearly greater than that of the free passage hollowed out in the ring 12.

La face supérieure de la marge débordante de la semelle 14, c'est-à-dire sa face tournée vers l'anneau 12, est revêtue d'un coussin annulaire 15 en caoutchouc ou matériau élastique analogue.The upper face of the protruding margin of the sole 14, that is to say its face facing the ring 12, is coated with an annular cushion 15 of rubber or similar elastic material.

Un manchon 16, également constitué en caoutchouc ou analogue, est prévu sur la face périphérique, du pied 13 ou de la semelle 14, susceptible de venir buter radialement contre une portée en regard : c'est le cas de la semelle 14 sur la figure 1 et de la base du pied 13 raccordée à la semelle sur la figure 2.A sleeve 16, also made of rubber or the like, is provided on the peripheral face of the foot 13 or of the sole 14, capable of abutting radially against a facing bearing: this is the case of the sole 14 in the figure 1 and of the base of the foot 13 connected to the sole in FIG. 2.

Le jeu radial j entre le pied 13 et l'anneau 12 doit être suffisant pour que le passage du liquide amortisseur à ce niveau ne soit pas étranglé au point de dérégler le fonctionnement de l'amortisseur.The radial clearance j between the foot 13 and the ring 12 must be sufficient so that the passage of the damping liquid at this level is not throttled to the point of adjusting the operation of the shock absorber.

Ce jeu doit par contre être assez petit pour que l'anneau 12 puisse jouer efficacement son rôle de butée, précisé ci-après, dans toutes les directions.This game must on the other hand be small enough so that the ring 12 can effectively play its role of abutment, specified below, in all directions.

Dans le mode de réalisation préféré illustré, l'anneau 12 est constitué, non pas par une simple rondelle plate, mais par une rondelle plate intérieure 121 raccordée à une rondelle plate extérieure 122 décalée axialement par rapport à la rondelle intérieure, par l'intermédiaire d'une portion de raccordement annulaire 123 présentant un profil en S.In the preferred embodiment illustrated, the ring 12 is formed, not by a simple flat washer, but by an inner flat washer 12 1 connected to an outer flat washer 12 2 axially offset with respect to the inner washer, by l 'through an annular connection portion 12 3 having an S profile.

Cette construction en forme de cuvette renversée permet à la fois :

  • - de placer à l'intérieur de la paroi tronconique 6 la rondelle plate intérieure 121 qui constitue la partie active de l'anneau 12 travaillant en butée,
  • - et de monter l'anneau 12 à l'intérieur du support par simple serrage axial de sa rondelle plate extérieure 122 entre le rebord 111 du siège 11 et la paroi 6 ou plutôt le renfort annulaire 7 de cette paroi 6.
This inverted bowl-shaped construction allows both:
  • to place inside the frustoconical wall 6 the internal flat washer 12 1 which constitutes the active part of the ring 12 working in abutment,
  • - And to mount the ring 12 inside the support by simple axial tightening of its external flat washer 12 2 between the flange 111 of the seat 11 and the wall 6 or rather the annular reinforcement 7 of this wall 6.

C'est le serrage axial de ces trois pièces (111, 122, et 7) ainsi que du pourtour de la paroi élastique 8, qui est assuré par sertissage extérieur de la virole 1.It is the axial tightening of these three parts (11 1 , 12 2 , and 7) as well as of the periphery of the elastic wall 8, which is ensured by external crimping of the ferrule 1.

Le rôle de la butée mutuelle entre l'anneau 12 et le pied 13 prolongé par la semelle 14 est joué de la façon suivante.The role of the mutual stop between the ring 12 and the foot 13 extended by the sole 14 is played in the following manner.

Dans le cas d'une sollicitation anormalement élevée du moteur vers le haut (selon la flèche F), la paroi 6 se déforme à la traction jusqu'à butée axiale de la portion débordante de la semelle 14 contre le bord de l'anneau 12.In the case of an abnormally high stress on the motor upwards (according to arrow F), the wall 6 deforms in traction until axial stop of the projecting portion of the sole 14 against the edge of the ring 12 .

Cette butée s'établit d'abord progressivement grâce à l'interposition du coussin 15, puis elle interrompt totalement la déformation en traction de la paroi 6 lorsque ledit coussin 15 est totalement écrasé.This stop is first established gradually through the interposition of the cushion 15, then it completely interrupts the tensile deformation of the wall 6 when said cushion 15 is completely crushed.

Dans le cas au contraire d'une forte sollicitation du moteur vers le bas (selon la flèche G), la paroi 6 commence par se déformer par compression et flexion en s'écrasant progressivement contre l'anneau 12 jusqu'à butée axiale finale du corps 3 lui-même contre ledit anneau.On the contrary, in the event of a strong downward bias on the motor (according to arrow G), the wall 6 com mence by deforming by compression and bending by gradually crushing against the ring 12 until final axial stop of the body 3 itself against said ring.

Enfin, dans le cas d'une sollicitation latérale horizontale (selon la flèche H) ou de basculement (selon la flèche K), c'est la tranche périphérique de la semelle 14 ou la paroi latérale de la base du pied 13 qui vient buter contre la portée transversale en regard du support avec encore une première phase d'écrasement élastique :

  • - dans le cas de la figure 1, pour laquelle le jeu j est relativement grand, la butée est établie entre la tranche de la semelle 14 et la zone incurvée 123 de l'anneau 12,
  • - dans le cas de la figure 2, qui fait apparaître un jeu j plus petit, la butée est réalisée entre la base du pied 13 et la tranche interne de la rondelle intérieure i21.
Finally, in the case of a horizontal lateral stress (according to arrow H) or tilting (according to arrow K), it is the peripheral edge of the sole 14 or the side wall of the base of the foot 13 which abuts against the transverse bearing surface facing the support with another first phase of elastic crushing:
  • in the case of FIG. 1, for which the clearance j is relatively large, the stop is established between the edge of the sole 14 and the curved zone 12 3 of the ring 12,
  • - In the case of FIG. 2, which shows a smaller clearance j, the stop is produced between the base of the foot 13 and the internal edge of the inner washer i 2 1 .

Ainsi, dans tous les cas où une sollicitation anormalement élevée est exercée sur le moteur supporté, par exemple dans le cas d'une décélération brusque du véhicule, on observe une interruption d'abord progressive et finalement extrêmement ferme et sûre des déformations de la paroi 6.Thus, in all the cases where an abnormally high stress is exerted on the supported motor, for example in the case of a sudden deceleration of the vehicle, one observes a initially progressive interruption and finally extremely firm and sure of the deformations of the wall 6.

En suite de quoi, et quel que soit le mode de réalisation adopté, on dispose finalement d'un support dont la constitution et le fonctionnement résultent suffisamment de ce qui précède.Following this, and whatever the embodiment adopted, there is finally a support whose constitution and operation result sufficiently from the above.

Ce support présente sur ceux antérieurement connus l'important avantage d'assurer un ancrage très solide de la première pièce rigide sur la seconde, c'est-à-dire, dans l'application citée à titre d'exemple, du moteur sur le châssis du véhicule, vu la limitation par butée élastique qui est imposée, dans un tel support, aux déformations de la paroi 6 lors de l'exercice de sollicitations anormalement élevées sur la masse supportée.This support has over those previously known the important advantage of ensuring a very solid anchoring of the first rigid part on the second, that is to say, in the application cited by way of example, of the motor on the chassis of the vehicle, in view of the limitation by elastic stop which is imposed, in such a support, on the deformations of the wall 6 during the exercise of abnormally high stresses on the supported mass.

Comme il va de soi, et comme il résulte d'ailleurs déjà de ce qui précède, l'invention ne se limite nullement à ceux de ses modes d'application et de réalisation qui ont été plus spécialement envisagés ; elle en embrasse, au contraire, toutes les variantes, notamment :

  • - celles où la semelle débordante 14 et son revêtement 15 seraient percés de trous ou encoches les traversant axialement de part en part, de façon à faciliter la libre circulation du liquide entre cette semelle et l'anneau 12,
  • - celles où les coussins de caoutchouc ou autre matière élastique destinés à amortir les chocs entre la butée centrale (pied et/ou semelle) et les portées en regard seraient prévus sur ces portées au lieu de l'être sur cette butée, ou en supplément à ceux prévus sur cette butée,
  • - celles où lesdits coussins, tout en demeurant de révolution autour de l'axe du support, auraient une épaisseur variable et non constante sur toute leur étendue,
  • - celles où le profil de la butée centrale (pied et/ou semelle) et/ou celui des portées en regard serait déterminé de façon à obtenir la progressivité voulue des différentes butées élastiques observées lors de l'exercice de sollicitations anormalement élevées sur la masse supportée, les faces en regard de l'anneau 12 et de la butée centrale 13, 14 pouvant en particulier être non plus planes, mais tronconiques, avec des angles de conicité identiques ou non, le demi-angle au sommet de chaque cône considéré, d'axe confondu avec celui du support, étant notamment de l'ordre de 60 à 80 degrés : dans ce dernier cas, la forme de la rondelle interne 121 est tronconique et se rapproche de celle de la face interne de la paroi tronconique 6.
As it goes without saying, and as it already follows from the above, the invention is in no way limited to those of its modes of application and embodiments which have been more specifically contemplated; on the contrary, it embraces all variants, in particular:
  • - those where the protruding sole 14 and its covering 15 are pierced with holes or notches passing through them axially right through, so as to facilitate the free circulation of the liquid between this sole and the ring 12,
  • - those where the cushions of rubber or other elastic material intended to absorb shocks between the central stop (foot and / or sole) and the facing spans would be provided on these spans instead of being on this stop, or in addition to those provided on this stop,
  • - those where said cushions, while remaining rotational around the axis of the support, would have a variable thickness and not constant over their entire extent,
  • - those where the profile of the central stop (foot and / or sole) and / or that of the facing spans would be determined so as to obtain the desired progressiveness of the various elastic stops observed during the exercise of abnormally high stresses on the mass supported, the opposite faces of the ring 12 and of the central stop 13, 14 being able in particular to be no longer flat, but frustoconical, with angles of conicity identical or not, the half-angle at the top of each cone considered, axis coinciding with that of the support, being in particular of the order of 60 to 80 degrees: in the latter case, the shape of the internal washer 12 1 is frustoconical and approaches that of the internal face of the frustoconical wall 6 .

Claims (6)

1. Dispositif antivibratoire destiné à être interposé aux fins de support et d'amortissement entre deux éléments rigides, constitué par un boîtier étanche interposé entre les deux éléments rigides, boîtier comportant deux pièces rigides (1-2, 3-5) solidarisables respectivement avec les deux éléments rigides, une première paroi élastique (6) reliant de façon étanche l'une des deux pièces rigides (3-5) à une armature angulaire (1 ) faisant partie de l'autre pièce (1-2) et assurant le rôle de support entre les deux pièces, une seconde paroi élastique (8) portée de manière étanche par l'armature annulaire (11), une cloison déformable (9) également portée de manière étanche par l'armature annulaire, entre les deux parois élastiques, et divisant l'intérieur du boîtier en deux chambres (A, B), savoir une chambre de travail (A) comprise entre la cloison déformable (9) et la première paroi élastique (6) et une chambre de compensation (B) comprise entre la cloison déformable (9) et la seconde paroi élastique (8), ces deux chambres communiquant entre elles par un passage étranglé (10), des moyens pour limiter à une amplitude faible, c'est-à-dire inférieure à 1 mm, les déformations de la cloison (9) selon la direction axiale perpendiculaire à son plan moyen, et une masse liquide remplissant les deux chambres ainsi que le passage étranglé, caractérisé en ce qu'il comprend un anneau rigide (12) porté par l'armature annulaire (11), entre la cloison déformable (9) et la première paroi élastique (6), anneau dont le bord interne plonge dans la chambre de travail (A) , et un pied (13) prolongeant la première pièce rigide (3) vers l'intérieur de la chambre de travail, pied traversant avec jeu l'anneau rigide (12) et terminé au-delà de cet anneau par une semelle débordante (14) dont la section droite est supérieure à la section de passage de l'anneau.1. Antivibration device intended to be interposed for the purposes of support and damping between two rigid elements, constituted by a sealed housing interposed between the two rigid elements, housing comprising two rigid parts (1-2, 3-5) which can be secured respectively with the two rigid elements, a first elastic wall (6) sealingly connecting one of the two rigid parts (3-5) to an angular frame (1) forming part of the other part (1 - 2) and ensuring the role of support between the two parts, a second elastic wall (8) carried in a sealed manner by the annular frame (1 1 ), a deformable partition (9) also carried in a sealed manner by the annular frame, between the two walls elastic, and dividing the interior of the housing into two chambers (A, B), namely a working chamber (A) between the deformable partition (9) and the first elastic wall (6) and a compensation chamber (B) between the deformable partition (9) and the second e elastic wall (8), these two chambers communicating with one another by a constricted passage (10), means for limiting the deformations of the partition (9) to a small amplitude, that is to say less than 1 mm in the axial direction perpendicular to its mean plane, and a liquid mass filling the two chambers as well as the constricted passage, characterized in that it comprises a rigid ring (12) carried by the annular reinforcement (1 1 ), between the deformable partition (9) and the first elastic wall (6), ring whose internal edge plunges into the working chamber (A), and a foot (13) extending the first rigid part (3) towards the interior of the chamber work, foot crossing with clearance the rigid ring (12) and terminated beyond this ring by an overflowing sole (14) whose cross section is greater than the passage section of the ring. 2. Dispositif- selon la revendication 1, caractérisé en ce que les faces, du pied (13) et/ou de la semelle (14), susceptibles de venir en butée contre des portées en regard de l'anneau rigide (12) ou d'autres composants du support, sont revêtues d'un coussin (15, 16) en caoutchouc ou matériau analogue.2. Device according to claim 1, characterized in that the faces of the foot (13) and / or of the sole (14), capable of abutting against bearing surfaces facing the rigid ring (12) or other components of the support, are covered with a cushion (15, 16) of rubber or similar material. 3. Dispositif selon l'une quelconque des revendications 1 et 2, caractérisé en ce que le pied (13) est constitué par un pion cylindrique et la semelle (14), par une plaquette rapportée axialement sur l'extrémité libre de ce pion.3. Device according to any one of claims 1 and 2, characterized in that the foot (13) is constituted by a cylindrical pin and the sole (14), by a plate attached axially to the free end of this pin. 4. Dispositif selon l'une quelconque des précédentes revendications, caractérisé en ce que l'anneau rigide comporte une rondelle plate intérieure (121) disposée à l'intérieur de la première paroi élastique (6) et raccordée par une portion annulaire (123) incurvée en S à une rondelle plate extérieure (122) décalée axialement par rapport à la rondelle intérieure et serrée axialement entre la première paroi élastique et la portion périphérique (111) du siège de la cloison déformable (9).4. Device according to any one of the preceding claims, characterized in that the rigid ring comprises an internal flat washer (12 1 ) disposed inside the first elastic wall (6) and connected by an annular portion (12 3 ) curved in S to an outer flat washer (12 2 ) offset axially with respect to the inner washer and clamped axially between the first elastic wall and the peripheral portion (11 1 ) of the seat of the deformable partition (9). 5. Dispositif selon l'une quelconque des précédentes revendications, caractérisé en ce que les faces en regard de l'anneau rigide (12) et de l'ensemble pied (13)-semelle (14) sont tronconiques.5. Device according to any one of the preceding claims, characterized in that the opposite faces of the rigid ring (12) and of the foot (13) -sole (14) assembly are frustoconical. 6. Dispositif selon la revendication 5, caractérisé en ce que les angles de conicité des faces en regard sont identiques, le demi-angle au sommet du cône considéré étant de l'ordre de 60 à 80 degrés.6. Device according to claim 5, characterized in that the angles of conicity of the facing faces are identical, the half-angle at the top of the cone considered being of the order of 60 to 80 degrees.
EP85400815A 1984-05-04 1985-04-25 Hydraulic antivibration mounting Expired EP0165095B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85400815T ATE31353T1 (en) 1984-05-04 1985-04-25 HYDRAULIC ANTI-VIBRATION BEARING.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8406986 1984-05-04
FR8406986A FR2563879B1 (en) 1984-05-04 1984-05-04 HYDRAULIC ANTIVIBRATORY SUPPORT

Publications (2)

Publication Number Publication Date
EP0165095A1 true EP0165095A1 (en) 1985-12-18
EP0165095B1 EP0165095B1 (en) 1987-12-09

Family

ID=9303712

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85400815A Expired EP0165095B1 (en) 1984-05-04 1985-04-25 Hydraulic antivibration mounting

Country Status (10)

Country Link
US (1) US4607828A (en)
EP (1) EP0165095B1 (en)
JP (1) JPS6162633A (en)
AT (1) ATE31353T1 (en)
BR (1) BR8502113A (en)
CA (1) CA1245206A (en)
DE (1) DE3561172D1 (en)
ES (1) ES295833Y (en)
FR (1) FR2563879B1 (en)
ZA (1) ZA853177B (en)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0174184A2 (en) * 1984-09-07 1986-03-12 Bridgestone Corporation Vibration isolating apparatus
EP0183251A2 (en) * 1984-11-29 1986-06-04 METZELER Gesellschaft mit beschränkter Haftung Elastic engine mounting with hydraulic damping
EP0194035A2 (en) * 1985-02-28 1986-09-10 General Motors Corporation Hydraulic-elastomeric vehicle engine mount
FR2589208A1 (en) * 1985-10-28 1987-04-30 Hutchinson Sa IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS
FR2592114A1 (en) * 1985-12-24 1987-06-26 Hutchinson Sa IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS
DE3700589A1 (en) * 1986-01-10 1987-07-16 Bridgestone Corp VIBRATION DAMPER
FR2604231A1 (en) * 1986-09-19 1988-03-25 Peugeot Hydroelastic support, especially for the suspension of a motor vehicle engine
EP0271894A2 (en) * 1986-12-19 1988-06-22 METZELER Gesellschaft mit beschränkter Haftung Hydraulically damping motor mount
EP0313462A1 (en) * 1987-10-23 1989-04-26 Hutchinson Hydraulic antivibration mounts
WO1996004492A1 (en) * 1994-08-05 1996-02-15 Lord Corporation Fluid damping devices

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0756314B2 (en) * 1985-02-27 1995-06-14 株式会社ブリヂストン Anti-vibration device
JPS63266238A (en) * 1987-04-17 1988-11-02 Tokai Rubber Ind Ltd Fluid seal type mount device
FR2619179B1 (en) * 1987-08-03 1989-12-22 Hutchinson IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS
JPS6465345A (en) * 1987-09-03 1989-03-10 Tokai Rubber Ind Ltd Fluid-sealed type mount device
US4836513A (en) * 1988-03-16 1989-06-06 The Goodyear Tire & Rubber Company Hydraulically damped anti-vibration mount with a flexible flap as a dynamic rate inhibitor
DE3808996A1 (en) * 1988-03-17 1989-09-28 Metzeler Gmbh HYDRAULIC DAMPING TWO CHAMBER - ENGINE MOUNT
US4925162A (en) * 1988-06-17 1990-05-15 Bridgestone Corporation Vibration isolating devices
US4880215A (en) * 1988-08-05 1989-11-14 Tokai Rubber Industries, Ltd. Fluid-filled elastic mounting structure
JPH0625727Y2 (en) * 1988-08-23 1994-07-06 東海ゴム工業株式会社 Fluid-filled mounting device
JP2804778B2 (en) * 1989-03-03 1998-09-30 株式会社ブリヂストン Anti-vibration device
JPH0716126Y2 (en) * 1989-03-31 1995-04-12 東海ゴム工業株式会社 Fluid-filled mounting device
FR2650355B1 (en) * 1989-07-28 1994-01-28 Paulstra Gmbh IMPROVEMENTS ON VIBRATION DAMPING DEVICES
US5351138A (en) * 1990-04-24 1994-09-27 Ricoh Company, Ltd. Image area discriminating device
JPH06105096B2 (en) * 1990-06-12 1994-12-21 東海ゴム工業株式会社 Fluid-filled mount device and manufacturing method thereof
JPH0446245U (en) * 1990-08-23 1992-04-20
DE4216185C2 (en) * 1992-05-15 1994-12-08 Boge Gmbh Elastic rubber bearing
JP2799953B2 (en) * 1993-07-06 1998-09-21 山下ゴム株式会社 Liquid ring vibration isolator
US5772189A (en) * 1995-06-15 1998-06-30 Yamashita Rubber Kabuskiki Kaisha Antivibration rubber device
JP3166493B2 (en) * 1994-06-28 2001-05-14 豊田合成株式会社 Liquid filled vibration isolator
JP3487123B2 (en) * 1997-03-18 2004-01-13 東海ゴム工業株式会社 Fluid-filled vibration isolator
FR2766889B1 (en) * 1997-08-01 1999-10-08 Hutchinson HYDRAULIC ANTIVIBRATORY SUPPORT
US6502883B2 (en) 2000-12-04 2003-01-07 Cooper Technology Services, Llc Two stage body mount rebound cushion
EP1283376B1 (en) * 2001-08-07 2005-06-08 Hutchinson Hydraulic damping support
US6712345B2 (en) * 2001-08-24 2004-03-30 Delphi Technologies, Inc. Powertrain mount with high frequency plunger

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2380899A (en) * 1944-01-21 1945-07-31 Lord Mfg Co Mounting
FR2155594A5 (en) * 1971-10-07 1973-05-18 Daimler Benz Ag
DE2514295A1 (en) * 1975-04-02 1976-10-21 Continental Gummi Werke Ag Resilient mounting for vehicle engines - has air cushion comprising piston and cylinder sealed by rolling bag
US4159091A (en) * 1976-06-30 1979-06-26 Automobiles Peugeot Damper device, in particular for the suspension of an engine
DE3016421A1 (en) * 1980-04-29 1981-11-05 Phoenix Ag, 2100 Hamburg Elastic engine bearer with hydraulic damping - has variable volume chamber formed by rubber balloon inside inner member
DE8119912U1 (en) * 1981-07-08 1982-07-08 Boge Gmbh, 5208 Eitorf Elastomer bearings, especially single-chamber rubber bearings with hydraulic damping
DE3239787A1 (en) * 1982-10-27 1983-09-08 Daimler-Benz Ag, 7000 Stuttgart Elastic bearing, in particular for bearing an internal combustion engine in a motor vehicle
EP0088682A1 (en) * 1982-03-03 1983-09-14 Hutchinson Hydraulic diaphragm dampers

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2519702A (en) * 1946-09-24 1950-08-22 Cecil S Robinson Duplex spring absorption unit

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2380899A (en) * 1944-01-21 1945-07-31 Lord Mfg Co Mounting
FR2155594A5 (en) * 1971-10-07 1973-05-18 Daimler Benz Ag
DE2514295A1 (en) * 1975-04-02 1976-10-21 Continental Gummi Werke Ag Resilient mounting for vehicle engines - has air cushion comprising piston and cylinder sealed by rolling bag
US4159091A (en) * 1976-06-30 1979-06-26 Automobiles Peugeot Damper device, in particular for the suspension of an engine
DE3016421A1 (en) * 1980-04-29 1981-11-05 Phoenix Ag, 2100 Hamburg Elastic engine bearer with hydraulic damping - has variable volume chamber formed by rubber balloon inside inner member
DE8119912U1 (en) * 1981-07-08 1982-07-08 Boge Gmbh, 5208 Eitorf Elastomer bearings, especially single-chamber rubber bearings with hydraulic damping
EP0088682A1 (en) * 1982-03-03 1983-09-14 Hutchinson Hydraulic diaphragm dampers
DE3239787A1 (en) * 1982-10-27 1983-09-08 Daimler-Benz Ag, 7000 Stuttgart Elastic bearing, in particular for bearing an internal combustion engine in a motor vehicle

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0174184A2 (en) * 1984-09-07 1986-03-12 Bridgestone Corporation Vibration isolating apparatus
EP0174184B1 (en) * 1984-09-07 1993-05-19 Bridgestone Corporation Vibration isolating apparatus
EP0183251A2 (en) * 1984-11-29 1986-06-04 METZELER Gesellschaft mit beschränkter Haftung Elastic engine mounting with hydraulic damping
EP0183251A3 (en) * 1984-11-29 1986-10-08 Metzeler Kautschuk Gmbh Elastic engine mounting with hydraulic damping
EP0194035A3 (en) * 1985-02-28 1989-02-08 General Motors Corporation Hydraulic-elastomeric vehicle engine mount
EP0194035A2 (en) * 1985-02-28 1986-09-10 General Motors Corporation Hydraulic-elastomeric vehicle engine mount
FR2589208A1 (en) * 1985-10-28 1987-04-30 Hutchinson Sa IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS
EP0225227A1 (en) * 1985-10-28 1987-06-10 Hutchinson Modifications of hydraulic anti-vibration mountings
FR2592114A1 (en) * 1985-12-24 1987-06-26 Hutchinson Sa IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS
EP0228967A1 (en) * 1985-12-24 1987-07-15 Hutchinson Modifications to hydraulic anti-vibration mountings
DE3700589A1 (en) * 1986-01-10 1987-07-16 Bridgestone Corp VIBRATION DAMPER
FR2604231A1 (en) * 1986-09-19 1988-03-25 Peugeot Hydroelastic support, especially for the suspension of a motor vehicle engine
EP0271894A2 (en) * 1986-12-19 1988-06-22 METZELER Gesellschaft mit beschränkter Haftung Hydraulically damping motor mount
EP0271894A3 (en) * 1986-12-19 1989-05-31 METZELER Gesellschaft mit beschränkter Haftung Hydraulically damping motor mount
EP0313462A1 (en) * 1987-10-23 1989-04-26 Hutchinson Hydraulic antivibration mounts
FR2622267A1 (en) * 1987-10-23 1989-04-28 Hutchinson IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS
WO1996004492A1 (en) * 1994-08-05 1996-02-15 Lord Corporation Fluid damping devices

Also Published As

Publication number Publication date
JPS6162633A (en) 1986-03-31
EP0165095B1 (en) 1987-12-09
ZA853177B (en) 1986-06-25
ATE31353T1 (en) 1987-12-15
DE3561172D1 (en) 1988-01-21
CA1245206A (en) 1988-11-22
US4607828A (en) 1986-08-26
ES295833Y (en) 1988-01-01
ES295833U (en) 1987-07-01
FR2563879B1 (en) 1988-08-26
BR8502113A (en) 1985-12-31
FR2563879A1 (en) 1985-11-08

Similar Documents

Publication Publication Date Title
EP0165095B1 (en) Hydraulic antivibration mounting
EP0191703B1 (en) Hydraulic antivibration mounts
EP0787266B1 (en) Hydraulic vibration-damping mounting
EP0409707A1 (en) Hydraulic antivibration devices
EP0223712B1 (en) Modifications of hydraulic dampers
EP0359655B1 (en) Hydraulically damped bushings
WO1986003813A1 (en) Hydraulic anti-vibration support
FR2828540A1 (en) HYDRAULIC ANTIVIBRATORY SUPPORT
EP0225227B1 (en) Modifications of hydraulic anti-vibration mountings
EP0875692B1 (en) Damping device
EP0297974B1 (en) Hydraulic damping mounts
EP2282076B1 (en) Anti-vibration device for a vehicle and vehicle including such a device
FR2610054A1 (en) IMPROVEMENTS TO HYDRAULIC ANTIVIBRATORY SUPPORTS
EP0255434A1 (en) Hydraulic damping mountings
EP0305246B1 (en) Hydraulic damping supports
EP0378464B2 (en) Modifications of hydraulic antivibration devices
EP0511907A1 (en) Improvements to hydraulic anti-vibration devices
EP0849494B1 (en) Elastic hydraulic support in particular for the mounting of an engine in an automotive vehicle
FR2832477A1 (en) Hydrodynamic insulating snubber for motor vehicle engine has snubber body with expansion chamber defined by elastomeric mass and above central armature
FR2635155A1 (en) Improvements to the elastic supports including stop means
FR2555273A1 (en) Improvements made to hydraulic anti-vibration supports
EP1293701B1 (en) Antivibration support and antivibration device comprising the same
EP0845617B1 (en) Anti-vibration support, and vehicle with such a support
FR2714947A1 (en) Modification to hydraulic anti=vibration mounts for engine mounts
EP0961048B1 (en) Hydraulic damping support

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH DE GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19860203

17Q First examination report despatched

Effective date: 19870220

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 31353

Country of ref document: AT

Date of ref document: 19871215

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3561172

Country of ref document: DE

Date of ref document: 19880121

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: CONTINENTAL GUMMI-WERKE AKTIENGESELLSCHAFT

Effective date: 19880908

NLR1 Nl: opposition has been filed with the epo

Opponent name: CONTINENTAL GUMMI-WERKE AKTIENGESELLSCHAFT

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19920320

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19920409

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 19920413

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19920421

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19920424

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19920428

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19920429

Year of fee payment: 8

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19920430

Year of fee payment: 8

EPTA Lu: last paid annual fee
RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT REVOKED

27W Patent revoked

Effective date: 19921202

GBPR Gb: patent revoked under art. 102 of the ep convention designating the uk as contracting state

Free format text: 921202

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

NLR2 Nl: decision of opposition
EUG Se: european patent has lapsed

Ref document number: 85400815.8

Effective date: 19930331

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO